Stress Analysis

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JBSracing

JBSracing

Joined
Nov 28, 2004
Messages
158
For the nerds among us – You may enjoy a look at the following videos of Husaberg engine components under FEA load simulation.

These two are of the OEM and the new JBS Racing Conrod. Our new rod will be released soon, it is 10% heavier and 40% stronger than the stock rod. At the load being imposed here which is a simulation of a 700cc at 10,000 RPM the OEM rod has a safety factor of 1.07 I.e. its with in a few percent of braking, the JBS rod has safety factor of 1.51 – They’re about 1.5mb each.

http://www.jbsracingpage.co.uk/JBS%20Conrod.avi
http://www.jbsracingpage.co.uk/OEM%20Conrod.avi

This is a simulation of the crank at about 90° ATDC on the power stroke. This is the least accurate simulation of the 4 but gives an idea of what happens. This about 2mb.

http://www.jbsracingpage.co.uk/JBS%20Crank.avi

This is a simulation of the JBS Racing 105mm piston under maximum cylinder pressure. This is about 10mb.

http://www.jbsracingpage.co.uk/JBS%20105mm%20Piston.avi

Ben
[email protected]
www.jbsracing.co.uk
 
Ben,

That's about as close to **** as I can get without it actually being ****!!!

Thanks for sharing!

-Luke
 
hi ben

most fascinated by the crank? it appears to be weakest in the corner of the journal? although it shows a twisted crank it remains blue so i'm not sure how that works?

that will explain the mains going .....

both rod graphs go to the same max/min but yours seems to do well and have a slight tinge of red halfway round the small end. the OEM rod is weakest under the neck and i've seen three rods gone and that is exactly where they go!

couldn't upload the piston MS MP vid?

regards

Taffy
 
"couldn't upload the piston MS MP vid? "
Me neither. wouldn`t play anyway.
Very interesting, All the stress on the rod is at the small end as shown.
 
Ben. Brilliant! From your experience, when they fail, does it start from the point indicated in the analysis? If not, the analysis must have missed something. I have not seen enough broken ones to know.

Are the assumptions close enough to the real world for the loading case for the rods? The analysis appears to only have been done in tension between the ends. If you include dynamic loads, maximum stess areas can move considerably as you increase speed. At 10000 RPM the rod is going through some pretty severe accelerations in lots of directions.

I would have thought you should see higher stresses in the flanges of the I section around the lower middle of the rod due to the acceleration forces trying to bend it front-to-rear.
 

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